Tying mechanism for balers



Dec. 16, 1952 M. E. MGCLELLAN EI'AL 2,521,588

TYING MECHANISM FOR BALERS 9 Sheets-Sheet 1 Filed Aug. 6, 1949 INVENTORS M.E. McQLELLAN, .G.CHEATUM gag-1am.

ATTORNEYS Dec. 16, 1952 M. E. MCCLELLAN EI'AL 2,621,588

TYING MECHANISM FOR BALERS 9 Sheets-Sheet 2 Filed Aug. 6, 1949 INVENTORS M. .McCLELLAN, LG.CHEATUM a G.B.Hl BY ATTORNEYS 1952 M. E. MOCLELLAN ETAL TYING MECHANISM FOR BALERS 9 Sheets-Sheet 5 Filed Aug. 6, 1949 5 $5 -J Bw wmw E km R INVENTORS M.E.McCLELLAN, L.G. CHEATUM a GI.B.HIL

ATTORNEYS Dec. 16, 1952 M. E. M CLELLAN AL TYING MECHANISM FOR BALERS 9 Sheets-Sheet 4 Filed Aug. 6, 1949 FIG. 20 1 INVENTORS M.E.MCCLELLAN, L.G.OHEATUM 8\G.B.H|L L ATTORNEYS Dec. 16, 1952 M. E. M CLELLAN El'AL 2,621,583

. TYING MECHANISM FOR BALERS Filed Aug. 6, 1949 s Sheets-Sheet e 78 M.E.McCLELLA BIVGCHEATUM as. .HI I

Dec. 16, 1952 M. E. MCCLELLAN EI'AL 2,621,588

TYING MECHANISM FOR BALERS 9 Sheets-Sheet '7 Filed Aug. 6, 1949 DQQL 1952 M. E. MCCLELLAN ETAL 2,621,588

TYING MECHANISM FOR BALER-S 9 Sheets-Sheet 8 Filed Aug. 6, 1949 V INVENTORS ME. MCCLELLAN, BY L.G.CHEATUM a 6.8. IL

1952 M. E. MQCLELLAN ETAL 2,621,538

TYING MECHANISM FOR BALE-RS Filed Aug; 6, 1949 9 Sheets-Sheet 9 FIG. /5

INVENTORS M. E. McCLELLAN L G. CHEATUM a G./: HIL;

Patented Dec. 16, 1952 ED STATE TE T OF 2,621,588 'ry nc nonANIsM FOR BALE-BS Marcus is. McClellan and Leo Cheatum, Ottumwa, Iowa, and George B. Hill, New Hol land, Bag assignors to Deere Manufacturing Co; Iowa, a corporation of'lowa Appiication August 6, 1949, Serial No. 1 9,,(i28

1 This invention relates to an automatic baler or like machine. More particularly, theinvention relates to improved means for coordinating the various functions of the baler 'so as to obtain the most desirable ope'ration'ale'fiect's oftht various baling components, especially the bale-forming means and the bale-tying meansj l Although the principles of the invention, as will be'subsequently brought out herein, are applicable to balers of all types, the preferred'embodiment of the invention'on which the disclosure is based is intended primarily foruse in an agri.- cultural baler ofthe type utilized to pickup hay, straw o'rother cut crop material; and to feed such materialize means by which bales are formed, and subsequently tied and then ejected. In theusual type of machine for this purpose, the baler is mobile and is propelled by a tractor or other suitable source of draft power. The operating parts of the baler may derive power from a power source in the form of an internal combustion engine carried directly by the baler or from a power source deriving power in the first instance from the power take-01f shaft of the propelling tractor.

One of the principal objects 'ofthe present invention is to provide improved tying mechanism which is normally disposed in a position relatively remote from the bale case while the bale is bein formed and which is shiftable to a position relatively close to the bale case after the bale is formed, so that the-tying medium may be wrapped around the bale and tied without unnecessary. and undesirable slack. A further important object related to the foregoing object is the provision of means for guiding thetying-medium, which may be either wire or twine, during functioning of the baler while the tying mechanism is in its relatively remote position. A still further object is to provide operating means for the tying mechanism which renders the tying mechanism idle during formation of the bale, and to include driving mechanism which sequentially places the tying mechanism in tying position and effects mobilization of the tying mechanism drive means.

Further objects are to provide: Improved means for guiding a needle or other strand-carrying means across the bale case and at one end of the bale; improved means for guiding thencedle, preferably through tracks or guides-in the plunger; means for holding the plunger on its compression stroke so that the needle may pass through the guides or tracks and meansfor holding the wire or twine alwaysin readiness-to be tied, so t in the event of failure of the tying 9 Claims. (01. o c -ii 2 mechanism to function, it will not be necessary to re-thread the needle.

The foregoing and other important objects inherent in and encompassed by the-invention will become apparent to those skilled in the art as the following detailed description and accompanying sheetsof drawings disclose a preferred embodiment of the invention. a

In the drawings: Figure-'1 is a side elevational view oi a pick-up Figure 2 is a plan view of the pick-up baler; Figure 3 is a rear elevational view of the pick-up baler;

" Figure 4 is an enlarged sectional view of the driving mechanism for the bale-forming means and the tying means, the view being taken substantiaily along "the line 4-4 of" Figure 3;

Figure 5 is an enlarged fragmentary view, partly in section as viewed along the line 5- -5 of Figure 2, showing the structure'an'd illustrating the operation of the tying mechanism;

Figure 6 is a View similar to Figure 5 but showing another stage in the operation of the tying mechanism;

' Figures 7-10 are diagrammatic illustrations showing successive stages in the forming and tyingofabale;

Figure 11 is a front elevational view of the baling mechanism separated from the material:- feeding means, as viewed substantially along the line i IH of Figure 1; several extraneous'components having been omitted-from the'fig'ur'e for the purposes of clarification;

Figure 12 is a schematic view showing the arrangement of the control means as embodied in afluid-pr'essure control system;

Figure 13 is a sectional view, on an enlarged scale, of the control valve illustrated in Figure 12, Figure 1'3'illus'trating the movable valve member ina different position; i

Figure 14 is a fragmentary plan elevational view or part of the mechanism that initiates actuation of thecontrol means;

Figure 15 is a perspective view of part of the mechanism shown'in Figure li, as viewed in the direction of the-arrows on the line l 5l 5 of Fig- .ure14; r

Figure 16 is aperspective view of another portion ofthe mechanism shown in Figure 14,- the view-being taken" in the-direction of the arrows on thelin'e lfil,6 of Figureli;

Figure 1'? is an enlarged fragmentary sectional view italren 'substantially on the line |'6'-I6 of Figure '11 and illustrating part of the" motionacaipss 3 p l transmitting means between the drive means for the bale-forming means and the control means;

Figure 18 is an enlarged fragmentary sectional view taken substantially on the line I8l8 of Fi ure 3 and illustrating the connectible and disconnec-tible driving means for the tying means;

Figure 19 is an enlarged fragmentary sectional view of a portion of the tying mechanism as viewed along the line Iii-IQ of Figure 3;

Figure 20 is a top plan view of the plungerhead;

Figure 21 is an enlarged fragmentary sectional view of a lower portion of the bale case, showing the needle guide means, the needle, and a portion of the plunger, together with the wire-carrying means;

Figure 22 is a plan sectional view taken substantially along the line 22-22 of Figure 21;

Figure 23 is a fragmentary transverse sectional view taken on the line 2323 of Figure 22;

Figure 24 is an end elevational view, partly in section, as viewed along the line 2424 of Figure 22; and

Figure 25 is an enlarged fragmentary sectional view taken substantially along the line 2525 of Figure 21.

For the purposes of clarification of various details of the invention and the relation of these details to the particular baler chosen for purposes of illustration, the following description will proceed more or less on a basis of describing the various components as units with respect to their functional characteristics.

General baler construction-Figures 1, 2 and 3 (Reference numerals 25-40) The mobile baler illustrated herein comprises supporting structure including a transverse main frame 25 carried on transversely spaced apart wheels 26 and 21. The main frame has connected thereto a forwardly extending draft member 28 which may be suitably connected at its forward end to a tractor or other source of draft power.

The supporting structure also includes at the right-hand side of the baler means for handling material such as hay or straw picked up from the ground, this means including a pick-up unit 29 and a material-feeding unit 30.

Reference herein to rightand left-hand sides of the machine is to be considered with respect to the position of an observer standing behind the machine and looking forwardly.

The pick-up unit 29 may be of any suitable construction and is here shown as including a pick-up cylinder 3| which picks up material from the ground and transfers such material to a rearwardly and upwardly inclined platform 32. Endless belt conveyors 33 are provided for facilitating movement of the material rearwardly toward the feeding unit 30. The rear portion of the platform 32 narrows because of rearwardly converging side walls 34 so that the forward portion of the feeding unit 30 has a throat considerably narrower than the transverse width of the pickup cylinder 3 l. Another endless belt 35 assists in moving of the material" into the feeding unit 30. This unit may be of any suitable construction, that shown including means for preliminarily compacting or compressing the material, and for this purpose there are indicated in Figure 2, in dotted lines, a left-hand feeder belt 36 and a right-hand feeder belt 31. These belts are respectively carried on rollers mounted on vertical axes and including spring-loaded belt-tensioning devices 38 and 39 respectively. Since the feeding 4 mechanism illustrated may be of any suitable construction, and since it forms no part of the present invention, further detailed description thereof will not be made. Suffice it to say that the feeding mechanism, like the pick-up unit, is merely representative of appropriate means for effecting the feeding of material to bale-forming means to be described below.

The general baler construction includes part of the bale-forming means which comprises a bale case which is designated generally by the numeral 40 and which will be referred to briefly at this point for the purpose of completing the description of the manner in which the material is picked up from the ground and fed to the baleforming means.

Bale-forming meansFigures 7-11 and 20 (Reference numerals 40-52) The bale case is, as is more or less conventional, made up of a plurality of walls arranged to provide a rectangular and elongated baling chamber defined by top and bottom walls 4! and 42, front and rear walls 43 and 44 and a righthand end wall 45 (see also Figure 4) The front wall 43 is, of course, vertical and is disposed transversely with respect to the direction of travel of the baler. This front wall includes a rectangular feed opening 46 which is substantially in longitudinal alinement with the converging feeder belts 36 and 31 (Figure 2).

The bale-forming means further includes a bale-forming member here shown as a plunger 41 that is carried by the bale case 40 for reciprocation in a cycle including alternate compression and retraction strokes. The plunger may be of any suitable construction and is here shown as being in the form of a reenforced casting having a substantially flat leading or material-engaging face 48 and a hollow trailing portion that is provided with a bearing or pivot 49 for connection of the plunger 41 to driving means including as part thereof a reciprocating pitman or connecting rod 50, the means for driving which will be described subsequently.

In order that the illustrations in Figures 7-9 may be clarified, reference should be had to the top plan view of the plunger in Figure 20, wherein it is shown that the front face of the plunger is interrupted by a pair of transversely spaced, vertically running grooves 5|, each of which extends back toward the trailing edge of the plunger into an enlarged vertically extending guide or track 52. These guides and grooves are for the purpose of accommodating certain parts of the tying mechanism, reference to which will be made below.

As will be evident from an examination of Figures 7-10, material fed by the means 36 and 31 through the intake or feed opening 46 enters the bale case 40 in the path of the reciprocating plunger 41. In Figure '7, the plunger is shown at the end of its retraction stroke, so that the feed openin 46 is uncovered by the plunger. The beginning of the formation of a bale is designated by the legend E the material having already been compressed by a previous compression stroke of the plunger against a previous bale B which acts as a header for subsequent bales It will also be noted that the end of the compression stroke of the plunger 41, as indicated in Figure 8, coincides substantially with the lefthand vertical edge of the opening 46, whereupon the plunger at the end of its compression stroke covers the feed opening 46. In Figure 8, the

ears-8e formation of the bale B has been completed. Figure 9 is substantially a duplication of the illustration in Figure 8, with the exception of certain functions of the tying mechanism which will be brought out hereinafter. Figure 10 illustrates the completion of the tying operation on the bale B and the initiation of the formation of a new bale B Tying mechanism-in generaZ-Figures 1, 2, 3, 5-10, 19 and 25 (Reference numerals 53-107) The tying mechanism is a self-contained unit designated in the general illustration by the numeral 53 and comprises, basically, a housing 54 within which is enclosed appropriate gearing for twisting and kinking the tying wire. The particular details of the tying mechanism illustrated herein form no specific parts of the present invention and could very well be other than illustrated, except as will be pointed out below. Likewise, the tying mechanism need not handle wire but could as well handle twine or anyother suitable medium.

In so far as a disclosure of the particular tying mechanism illustrated is necessary to an immediate understanding of the present invention, the fundamental components thereof will be described. As best shown in Figure 19, the housing 54 contains a large gear 55 which is in constant mesh with a pair of twister gears'56, only one of which is shown but the presence of the other of which will be obvious from an inspection of Figure 19. Each of the gears 55 is slotted at El, and at times the slots 5! become alined with slots 58 in the bottom of the housing 5 3.

The housing 54 also carries a pair of transversely spaced apart vertical shafts 59 which will be hereinafter referred to as kinker shafts. These shafts project upwardly out of the casing 56 and have keyed thereto small pinions 88 which are respectively in constant mesh with opposite ends of a segmental gear 6!. The lower end of each kinker shaft includes a slotted kinking portion 62, only one of which appears in Figure 19. The drawing in Figure 19 has been broken out at the left-hand portion thereof to reveal a kinking portion 63 at the lower end of one of a second pair of kinker shafts which are plainly visible at 64 in Figures 1, 2 and 3.

The wire-twisting and wire-kinking means of the tying mechanism 53 is motivated by actuating means including a transverse shaft 65 journaled in a pair of bearings 66 carried on the top of the bale case 59 and spaced apart fore and aft as respects the direction of travel of the baler. This shaft has keyed thereto intermediate its ends a mutilated gear 51 which is intermittently engageable with a bevel pinion 68 keyed to a shaft 69 which extends at right angles to the shaft 65. The shaft 69 extends into the tier housing 54 and is splined to the large gear 55.

mechanism from within the casing or housing H. Such mechanism has not been illustrated specifically, since details thereof are unimportant here. The general idea can bereadily. perceived at 52 in Figure 1 and may include acam and spring-loaded plunger "intermittently enn 6 gageable in' timed relationship to effect inter. mittent rotation of the pinion -68.

The portion of the tying mechanism described so far is supplied with wire from a pair of staggered wire boxes I3 carried at an upper portion of the right-hand end of the bale case 48. These wire boxes may be replaced by and equivalent means; the type shown here is similar to that forming the subject matter of assigneescopending application, Serial No. 9,487; filed February 19, 1-948, and which issued as Patent 2,477,059,-'dated July 26, I949. 'Eachof the boxes 13 carries a coil of Wire C from each of which a strand of wire W is fed to the tying means '53. The wires W extend to the tying means'in spaced relation according to the spacing of theslots 58 in the housing 54.

Incidentally, the wire'boxes l3 have'beenom'itted from Figure -1 so as to expose the tying mechanism 53.

In the particular type of tying mechanism illustra'ted here, the housing 54 is 'positionablebetween an upper position, relatively remote from the bale case (Figure 5) and'a lower position, relatively close to the bale case (Figure 6). 'In'its former position, the housing 54 is-outof the way of a carrier 14 which-carries a pair of transversely spaced apart wire guides 15, these guides being spaced apart according to the spacing of the wires W. Although but one wire guide '15 is visible in the drawings, the presence'of both-in a typical construction will be readily perceived.

Each wire guide receives a pair of rollers 16 over which the proximate-wire'W is trained. As will be evident from Figure 7, each of the upper wires W extends downwardly through an opening M in the bale case-top wall 4| and-thence over the left-hand end of a bale to be formed. The wire W is unitedin a knot or tie K to'the free end of a cooperating lower wire W Thereare two wires W which are fed from a pair of coils C contained in a pair'of lower wire boxes 11 (Figure 3) carried'below the bale case 40. Although only one coil C and one wire box 11 appear in the drawings, the presenceof two of each will be readily apparent. The tying mechanism is provided with a lower wire guide arrangement 18 which, for present purposes,' may be assumed to be very similar to that provided at the top of the bale case (Figures l-l'O). The details of the lower guide arrangement -willbe brought out below in the description of Figures 2l-25.

The lower component of thetying mechanism includes strand-passing or -carrying means comprising a pair of vertically movableneedles lil, only one of which appears in the drawings. The bottom wall 42 of the bale case isopen at'42 and guide means, in the form of a needle-guidecasting 19, is provided for guiding the needles in their upward movement to the plunger tracks 52. Each needle is pivoted at its lower endat '88 to a control link 8| which is in turn pivoted at 82 to a bracket 83 carried at a rear righth'and portion of the main frame 25 (Figure '3) Oscillation of the needles is accomplished by a crank 84 keyed to a short shaft 85 at the rear of the *bale case 40. This shaft further has keyed thereto a sprocket 86 which is driven by meansof a '84 is slotted at 98 to develop proper control of the link 8l, -which is accomplished by-aoconnecting link 9| between the crank84 and the .control link 8 i.

The connection-of the link 9i to the crank 84 is effected by means of a connecting pin 92 passing through the slot 90 and a roller 93 which engages the surface of the cam 89.

It will be seen from the description thus far that rotation of the shaft 85 causes rotation of the crank 84 to move the needle from the positions shown in Figures 3 and '7 to the position shown in Figure 9. Since the needle is operated by means of the shaft 55, there will be a definite relationship between operation of the twisting and kinking mechanism and operation of the needle.

The upper portion of the needle is provided with a pair of wire-engaging rollers 94, which are spaced apart lengthwise of the lower wire W so as to engage this wire and bring it upwardly to be received by the twister gear 56 and kinkers 62 and 63 in the manner shown in Figure 9.

The functioning of the mechanism 53 and the needles 19 to eifect forming of the ties or knots K is accompanied by changes in position of the housing 54, as illustrated in Figures and 6. For this purpose, the shaft 55 carries a pair of spaced apart cams 95. These cams are keyed to the shaft 55 for rotation therewith and respectively engage rollers 96 on raising and lowering arms 91. Each arm 91 is pivoted at its righthand end at 98 to a bracket 99 carried on the top of the bale case 40. A U-shaped or bale member I00 is arranged so that its transverse portion or night lies closely adjacent the housing 54 and so that the legs thereof, designated at If, extend lengthwise of the bale case to pivotal connections by means of bearings I02 on the transverse shaft 65. The housing 54 is provided with a pair of ears 103 by means of which and bolts I04 the housing is mounted on the legs I01 of the bail I00.

The bale I00, and hence the housing 54, is

raised and lowered by the arms 91 through the medium of short connecting links I05.

The housing 54 includes a lower portion which is recessed at I06 to accommodate the upper portion of the needle 19 and this recessed portion further includes a track or guide I01 which complements the proximate track or guide 52 in the plunger 41. The track portion I01 is disposed at an angle to the vertical so that it occupies the position shown in Figure 6 and thereby forms substantially a continuation of the track 52 in the plunger.

The following is a brief and general description of the tying mechanism to the extent thus far described and to the extent believed necessary to expedite an understanding of the mechanism.

While the plunger 41 is reciprocating, the tying mechanism housing 54 is in its upper position, as illustrated in Figures 5, 7, 8 and 10. The plunger is forming the bale B and the upper and lower wires W and W which have been united at K are moved along to the left in the bale case. When the baler is first started without having been previously operated and there is no bale B in the bale case to act as a header, the tie or knot is performed manually at K. Pressure of the material to the left thuscarries the loop, formed by the united wires W and W to the left and the bale is gradually accumulated by the plunger until it reaches a predetermined size, the wires desirablevslack in the wires. When the bale reaches the desired size, the plunger 81 is caused to be held at the end of its compression stroke (by mechanism to be set forth below) Simultaneously, the shaft 65 is caused to operate (by mechanism to be described below) so that the cams 95-which have been holding the arms 91 in the raised position of Figure 5rotate in the direction or" the arrows (Figures 5 and 6) until the rollers 99 drop off onto the lower portions of the cams. Also, substantially simultaneously, means (to be described subsequently) operates to retract the wire guide carriers 14 and 18 to the right, thus moving these components respectively out from below the downwardly moving housing 54 and the upwardly moving needles 19.

Since the shaft 65 is connected by the sprockets 86 and 88 and chain 01 to the needle crankshaft 85, the needles will be actuated to move upwardly or vertically across the bale case through the needle guide casting 19 and thence through the needle guide tracks 52 in the plunger 51. As the needles move upwardly, they engage the loose intermediate portions of the lower Wires W and carry these portions upwardly, wire paying out from the lower coils C as this action takes place. When the upper housing has moved downwardly to the position of Figure 6, the upper wires W are received through the slots '58 in the housing 54 by the slotted twister gears 55 and. slotted kinkers 62 and 53. When the needle has moved upwardly to the position shown in Figure 6, the lower wires W have been carried up through the slots 53 to be received by the twister gears and kinkers. Upon lowering of the housing 54, the mutilated gear 61 has traveled through a sufficient angular range to incur rotation of the pinion 68, which causes actuation of the large gear 55 and consequently rotates the twister gears, the latter rotating preferably through four complete revolutions during the dwell period produced by the low portions on the cams 95. Following rotation of the twister gears, the means i2 causes reciprocation of the link 12 which in turn rocks the segmental gear 6| first in one direction and then in the other, thereupon incurring angular movement of the kinkers 62 and 63 first in one direction then in the other. The kinkers 52 and 53 are of the type which perform a wire-severing operation as a final stage in their wire-kinking operation, whereupon a second knot K (Figure 10) is formed at the right-hand end of the bale B Simultaneously, and since the twisted wires are severed intermediate the ends of the twisted portions, a third knot K is formed which again unites the wires W and W to provide a loop at the leading portion of the bale B about to be formed. In this respect, it should be noted that Figure 10 represents a stage in the bale-forming operation somewhat subsequent to that represented by Figure 9; that is to say, the occurrence of the accumulation of material represented at B takes place following the bale-tying operation and not during the bale-tying operation.

After completion of the bale-tying operation, the shaft 65 has rotated sufficiently to disengage the mutilated gear 11 from the pinion 68 and to cause the high portions of the cams 95 to again engage the rollers 95 for raising the arms 91 and hence the bail I0 and the housing 54. Also, the shaft has rotated sufiiciently to bring the roller 93 on the power-transmitting link 9i around to the other side of the cam 89, following which the needles 19 will be retracted from the accuses bale case 40 and will be freed from the needle guides 52 in the plunger 41.

The cam 89 is shaped as shown so that its upper portion is substantially flat, whereby rotation of the crankshaft 85 may continue without effecting withdrawal or retraction of the needles during the time that the wires are being twisted, kinked and severed. The shape of the cam 86 is, of course, not new in the present case and, as a matter of fact, any other suitable form of tyingmechanism-positioning means could be utilized in so far as the broad applicability of the invention is concerned.

Driving mechanismFigures 1-4 and 18 (Reference numerals 108-129) The source of power in the first instance in the type of baler illustrated is derived from the tractor or other propelling vehicle. For this purpose, the baler has a longitudinally extending propeller shaft I08 shown here as extending through the draft member 28, the latter being tubular for that purpose. The rear end of the propeller shaft I is connected by a suitable universal joint I09 (a portion of which is visible in Figure 1) to the forward end of a longitudinally extending shaft IIO. This shaft has keyed thereto a sheave III. Rotation of the sheave III and shaft H9 is in the direction indicated by the arrow in Figure 3. The shaft III] is suitably carried in appropriate bearings (not shown) in a longitudinal tubular member I I2 which forms part of the main frame 25.

The main frame 25 carries a second forwardly extending tubular member I I3 which is provided with suitable bearings (not shown) for journaling a longitudinally extending shaft I I4, the forward end of which is associated with suitable gearing II5 (Figure 1) for transmitting power to a transverse shaft II6 (Figures 1 and 2). The shaft I I6 extends to the left, as shown in Figure 2, and has keyed thereto a driving sheave I IT. A belt II8 connects, the sheave I I! and a sheave II9, the latter being appropriately connected by means (not shown) for driving a plurality of sheaves I20 for the belts 33 and 35. There is indicated in dotted lines in Figure 2 an idler sheave I2I for carrying that portion of the belt 35 within the feeding unit 39, the details of which are unimportant here.

The transverse shaft I16 serves, through the sheaves II! and H9 and belt IIB to drive the sheaves I20 which in turn drive the pick-up cylinder 3| through the belts 33. The :belt 35 is driven by the intermediate sheave I20 and is carried by the sheave I2I The latter is not carried by the transverse shaft I I6 but is slightly spaced thereabove.

The rear end of the shaft I I 4 has keyed thereto a first sheave I22 and a second and larger sheave I23. A belt I24 is trained about the sheaves III and I22 and a second belt I25 is trained about the sheave I23 and a smaller sheave I26 journaled on means including a casting or housing I2! at the right-hand end of the rear portion of the bale case 40. A sheave I28 is likewise journaled by the housing I21 and is. coaxial with the sheave I26. The sheaves I26 and I28 are relatively rotatable, the means for mounting which will be subsequently described.

The sheave I28 is connected to and drives a larger sheave I29 which is carried on the rear end of the shaft 65 by bearing means I39 so that the sheave I29 and shaft 65 are at times relatively rotatable (see Figure 18). The driving 10 means for interconnecting the sheaves I26 and I29 comprises a belt I3I.

The direction of rotation of the sheaves I28 and I29 is opposite to that of the sheaves III, I23 and I26, for reasons that will be explained below.

Clutch for tying mechanism-Figure 18 (Reference numerals 129-144) Part of the driving mechanism for connecting the source of power to the tying mechanism includes a connectible and disconnectible device between the sheave I29 and the tier shaft 65. A preferred form of such device is illustrated in the drawings as comprising a shiftable clutch member I32 which is carried for rotation with and shiftable axially with respect to the shaft 65 and which has engageableportions I33 selectively engageable with complementary portions I34 on the hub of the sheave I29. Additional supporting structure for the rear end of the shaft 65 is indicated generally by the numeral I 35: and is shown as being provided with a forward bearing I36 and a rearward bearing I31, the latter of which cooperates with the bearing I39 to carry the shaft 65 and the sheave I29.

As also shown in Figure 18, the sprocket 88 which is utilized to drive the needle crankshaft is pinned or may be otherwise secured to the shaft 65 for rotation therewith, as indicated at I38.

The support I35 includes at the right-hand side thereof a bracket I39 on which is mounted a clutch control arm I40, this arm being pivoted at I4I at its rear end and extending through the supporting structure to a conventional control connection with the shiftable clutch part I32. It will be evident that the arm, when in the position shown in Figure 18, is effective to maintain disengagement between the shaft 65 and sheave I29 and, when shifted to the rear (or to the left, as viewed in the drawings), is effective to establish driving connection between the shaft 65 and sheave I29.

The means for operating the arm I49 includes a fluid-receiving motordesignated generally by the numeral I42suitably mounted on the supporting structure I35 and effective. to shift the arm I40 in a counterclockwise direction, as viewed in Figure 18, through the medium of a motion-transmitting element I43. A compression spring I 44 serves as means for yieldably maintaining the indicated position of the control arm I40.

Further description of the arrangement and operation of the motor I42 will be included below in the description of the control mechanism.

Plunger and tier drive mechanism-Figure 4 (Reference numerals 47, '53 126, 128, '175) As previously stated, the sheaves I26 and I28 are mounted coaxially by means including the housing I2I. As shown in Figure the housing I 21' forms substantially the outer one-half of a complete housing structure including an inner housing part I45. The housing parts I27 and I45 are appropriately flanged and secured together and to the rear wall 44 of the bale case 40 as at I46. 1

The housing part I45 includes an inne'r'or forward wall I 4! which is formed with an integral sleeve I48 for the purpose ofjournaling the rear main bearing I49 of a crankshaft I50. The housingpart I45 further has formed integrally therewith a forwardly extending yoke II which has a flanged sleeve I52 secured to the inner or rear face of the front wall 43 of the bale case 40. The sleeve I52 journals the forward crank pin I53 of the crankshaft 50.

The crank I50 includes a single crank pin or throw I54 which is equipped with a partially spherical bearing I55 for efiecting an articulate connection with the plunger pitman 50.

The rear end of the main bearing I49 is provided with a pilot bearing I56 which carries the forward end of a shaft I51 to which the sheave I26 is keyed. Since the sheave I26 derives its power in the first instance from the propeller shaft I08, the shaft I51 will rotate continuously as long as the propeller shaft I08 is driven (barring, of course, acidental disconnection of intermediary driving components). The shaft I51 therefore constitutes a constantly operating input member and the crankshaft I50 constitutes an intermittently rotatable output member, the shaft I51 and chrankshaft I50 being, obviously, relatively rotatable, since one is piloted on the other.

The sheave I 28 forms part of a second intermittently rotatable output member which will be hereinafter designated as a whole by the numeral I26. This member includes, preferably as an integral part thereof, a circular drum portion I 58 which is substantially as large in diameter as'the housing part I21 and which has its inner annular surface machined to provide a braking surface I59. An inner portion of the member I28 is integrally formed as a sleeve I60 which is keyed at I6I to a quill I62 which has its inner or forward portion formed as a pinion I63. For most practical purposes, the pinion I63 may be considered an integral part of the output member or sheave I 28.

The housing part I21 includes a rear wall I64 which is centrally apertured to receive the quill I62 and which is provided with a bearin I65 for journaling the quill.

The constantly rotating shaft I51 passes loosely through the quill I62 and, in addition to being journaled or piloted in the rear end of the crankshaft I50, is journaled by means of a bearing I06 in the rear end of the member I28. The shaft I51 is therefore rotatable with respect to both the member I28 and the crankshaft I50 and the members I28 and I50 are rotatable relative to each other.

The pinion I63 forms part of means for interrelating the operation of the output members I28 and I50 for alternate operation so that the plunger may reciprocate while the tyin means is idle and the tying means may operate while the plunger is idle. The interrelating means preferably comprises an epicyclic gear train including, in addition to the pinion I63, a pinion I61 which is keyed or splined to the rear end of the crankshaft I50. The pinions I63 and I61 are spaced apart axially and the forward end of the shaft I51 extends across this space and has pinned thereto at I51a a carrier member I68, which preferably has some weight to serve as a flywheel for the crankshaft I50 when connected thereto, in a manner to be presently described.

The carrier I68 is provided at a point spaced radially from the axis of the shaft I51 with bearing means I69 for journaling a short shaft I to the rear end of which is keyed a small pinion IN. A substantially similar pinion I 12 is carried at the forward end of the shaft I10 for rotation with the shaft, being preferably formed as an integral part of the shaft. The pinion Ill is in constant mesh with the pinion I63. The pinion I12 is in constant mesh with the pinion I61. The pinions I63 and I61 are of slightly different sizes and, for present purposes, the pinion I61 may be taken as having twenty-eight teeth and the pinion I63 as having twenty-seven teeth. Likewise, the pinions HI and I12 are of different sizes. For present purposes, the pinion I12 has fourteen teeth and the pinion I1I has fifteen teeth. The relative differences in the sizes of the pinions account for the reversal of direction of the sheave I 28 with respect to the rotation of the constantly rotating or input sheave I26, as previously briefly referred to and as illustrated by the arrows in Figures 3 and 4.

The forward end of the crankshaft I50 in-- cludes a forward extension I13 which is keyed or otherwise fixed to the front main bearing I53 for rotation therewith. This member I13 extends forwardly through the sleeve I52 and an appropriate opening in the front bale case wall 43 to .carry a circular plate I14 which forms part of a holding or retaining means to be subsequently described.

Y A holding means for the output member I28 is here shown in the form of a brake I15. This brake may be of any conventional construction and is illustrated as being of the internalexpanding type engageable with the braking surface I50 which forms the annular interior of the drum I08. The means for actuating the brake, as well as the means for actuating the holdin means including the plate I14, will be subsequently described.

Brief description of the driving mechanism (Reference numerals 108, I26, 128, 145475) Power is constantly supplied by the propeller shaft I08 to the constantly rotating member I26, thereby constantly rotating the shaft I51 and the carrier I68 in a clockwise direction as viewed from the rear or to the left as indicated by the arrows in Figure 4. Normally the brake I15 will be energized or effective to lock or hold the drum I58 and consequently the output member I28 will be demobilized or maintained in a stationary condition. Demobilizing of the drum I58 results also in demobilizing of the pinion I 63, with the result that the pinion I1I, as it travels around the stationary pinion I63, transmits power through the shaft I10 to the pinion I 12 and thence to the crankshaft pinion I61, thereby rotating the crankshaft to reciprocate the pitman 50 and plunger 41. It will be appreciated, of course, that a considerable gear reduction is obtained and that, therefore, the speed of rotation of the crankshaft I50 will be appreciably lower than the speed of rotation of the input shaft I51.

By means of control mechanism to be subsequently described, the driving mechanism is permitted to continue in the operational status just described for a predetermined length of time, after which the brake I15 is released simultaneously with the application of a holding force on the plate I14. Such action results in a reversal of the power-transmitting effect of the epicyclic gear train so that the crankshaft I50 now becomes demobilized and the output member or sheave I28 becomes mobilized. Since the pinion I61 is now held stationary, the pinion I12, as it travels around the pinion I61, transmits power through the shaft I10 to th inion Ill and thence to the pinion I63. Because of the relative pitch diameters of the pinions, there will be a reversal of the direction of rotation of the output member I28. The member I28 will, like the crankshaft I58, be the recipient of the considerable gear reduction obtained through the epicyclic gear train. Hence, the speed of rotation of the output member I28 will be considerably below that of the constantly rotating sheave I29.

By means of the control mechanism to be subsequently described, the output member I28 is permitted to rotate through a predetermined phase dependent upon the operation of the tying means, after which the control mechanism sets up a reversal of the mobilizing and demobilizing effect of the holding means or brakes I14 and I15 so that another cycle of operation of the plunger is initiated while the tying means is idle. In this respect, it should be remembered that the tying mechanism clutch I32I34 is connected in series with the sheave I28 and shaft 65 and that the clutch is engaged substantially simultaneously with mobilizing of the sheave I28. For all practical purposes, the drive between the epicyclic gearing and the tying mechanism may be considered without the clutch, as if the sheave I29 were keyed directly to the shaft 65. However, as will be brought out below, the presence of the clutch I32I8:i is of importance as a safety feature, since it prevents operation of the tying means in the event of slippage of the brake I15, in which event some power would be transmitted by the sheave I28 to the tying means, which would be undesirable, inasmuch as the needles I9 would be projected into the bale case at a time when the plunger is reciprocating.

Control means- Figures 2 and 1117 (Reference numerals 142, 174-252) The circular plate I74 that is connected to the forward end of the plunger crankshaft I58, is provided with a relatively large first notch or cut-out portion I16, and with a second smaller notch Ill. The notch I'I' provides part of the control means, as will be subsequently set forth, and the notch I'll also provides part of the control means and comprises a subsidiary part of indexing or locking means including a beam or lever I18 which is pivoted intermediate its ends at I19 and which has at its lower end a lug I88 selectively engageable with or disengageable from the notch IT! in the plate I'M.

The upper end of the lever I18 is arranged to receive power from a fluid-receiving motor I8I which has a rod or link I82 engaging the lever. A compression spring I 83 provides means for normally maintaining the lug I88 on the lever I18 in engagement with or conditioned for engagement with the notch IT! in the plate I14.

The brake H at the rear end of the driving mechanism, which includes the epicyclic train, is under the control of a fiuid-pressure-receiving motor I84 (Figure 12). This brake, being of the internal-expanding type, is, as is conventional, normally relaxed by a tension spring (not shown).

As previously stated above in connection with the description of the tying mechanism, the wire guide carriers I4 and I8 are shiftable back and forth in timed relationship with raising and lowering of the tying mechanism gear housing 54 (Figures 5-10). The means for accomplishing the shifting of the wire guide carriers comprises a pair of fluid-pressure-receiving motors I85 and I86. For the purpo'se'of simplifying the disclosure, only the motor I appears in the diagrammatic illustration in Figure 12, but it will be understood that these motors are actuated simultaneously. Further, additional description of these motors will be directed primarily to the motor I85, it being understood that the motor I86 has similar parts, the details of which will be described below.

The motor I85 comprises a cylinder I81 within which is slidably carried a piston I88 having a piston rod I89, the outer end of which 'is'connected to the wire guide carrier I4. The motor I85 is of the two-way type and the interchange of fluid pressure therein effects shifting of the carrier in one direction or the other.

The motors I42, I8I, I84 and I85, for the tier clutch, index plate I14, brake I15, and wire guide carrier 14, respectively, are part of a fluidpressure system embodied in the control means. This system further includes a constantly running pump designated generally by the numeral I98. The pump includes a sheave I9I (Figures 3 and 12) which is in constant engagement with and driven by the drive belt I24. The pump is carried by an arm I92 pivotally mounted on a bracket I93 at the rear of the main frame 25. A tension spring I84 serves as means for maintaining the sheave I9I in engagement with the belt I24.

The pump I98 comprises part of a fluid-pressure source which also includes a fluid reservoir I95 mounted in any suitable manner on the rear of the baler. The pump draws fluid from the reservoir I95 through a conduit I96.

The pump supplies fluid under pressure through a conduit I9'I to a high-pressure passage I98 in a main control valve I98. The valve carries a shiftable valve member 288 formed with a lowpressure or return bore 28I which communicates with a low-pressure or return chamber 282 in the valve I89. The chamber 282 communicates with the reservoir I95 via a return conduit 283.

Fluid pressure is distributed by the valve I 89 to the motors I42, I8I, I84 and I85. Connection from the valve I99 to the motors IBI and I84 is made in parallel by a main conduit 284 and apair of branch conduits 285 and 288 leading respectively to the motors I8I and I84. A conduit 28'! leads to one end of the motor I85 and a conduit 288 leads to the other end of the motor I85 from the valve I99. A conduit 289 connects one end of the motor I85 in series with the motor I42.

The valve I99 and the shiftable valve member 288 are appropriately ported to accomplish the results to be set forth below. The arrangement is believed to be obvious from the drawings and no detailed description will be made of the arrangement of the ports.

In the position of the valve member in Figure 12, the fluid under pressure supplied by the pump I98 is distributed from the high-pressure passage I98 to supply the motors I8! and I84 and to supply the motor I85 through the conduit 288 so that the piston I88 is shifted in such manner that the wire guide carrier 74 will be in its extended position below the tier housing 54. Looking at Figure 12, the pressure applied to the motor I85 is such as to shift the piston I88 to the right. The righthand end of the cylinder I8! is exhausted through the conduit 28'! to the low-pressure bore 28I and low-pressure chamber 282 in the valve I99. At the same time, the motor I42 is exhausted through the conduit 299, through the cylinder I87 and through the conduit 28! to the chamber 282, and. thence to the reservoir I95. The piston in the motor I42 15 is in the position shown in Figure 12, because of the pressure applied by the spring I44 (Figure 18) The pump I90 includes a pressure-relief valve 2| 3 for obvious purposes.

When the control valve shiftable member 208 is in the position of Figure 12, the fluid-pressure motors I8I and I84 are under pressure, the former operating to pivot the lever I18 so that the lug I80 is disengaged from the notch I TI in the circular plate I14, and the latter operating to apply the brake I15 to the drum I58. Hence, the output member or sheave I28 to the tying mechanism is demobilized or held stationary, and the epicyclic gear train is effective to drive the crankshaft I50 for reciprocating the plunger 41. At the same time, the motor I85 for the wire guide carrier H4 is under pressure such as to extend the piston rod I89 so that the wire guide rollers I6 are in position below the tying mechanism casing or housing 54. Concurrently, the fluid-pressure motor I42 is exhausted through the conduit 209, the right-hand end (as viewed in Figure 12) of the cylinder I 88 and through the conduit 201 to the reservoir I95. Therefore, the tier clutch I 32I34 is disengaged. Since the operating parts are controlled in the manner aforesaid, the plunger is operating and the tying mechanism is idle. This status of the operation will continue until the control valve shiftable member 280 is shifted to a new position so that the ultimate result is to create a new operational status in which the plunger is idle and the tying mechanism operates. That portion of the control means that accomplishes the last mentioned result will be described below.

The front wall 43 of the bale case t!) carries a bearing ring 2I I (Figure 17) which surrounds the extension H3 at the forward end of the crankshaft I50 and which is therefore concentric with the axis of rotation of the crankshaft. This ring serves as means for mounting a control member which is in the form of a vertically elongated plate 2I2 (Figures 11 and 1'7). This plate is rockable within limits about the axis of the crankshaft and is connected to the shiftable control valve member 200 for the purposes of actuating the latter. The connection, as best shown in Figure 1'7, includes an upper rearwardly bent portion 2 l3 which has a downwardly bent ear 2 I4 pivotally connected to a clevis 2I5 at the right-hand end of the valve member 200 (left hand end as viewed in Figure 12). A tension spring 2IB provides means for maintaining the control plate 2I2 normally in such position that the shiftable valve member 290 occupies the position of Figure 12. One end of the spring is connected to the upper end of the control plate and the other end of the spring is connected to a plate '21 forming part of the front bearing 66 for the tier shaft 65.

The plate 2I2 is provided near its upper portion with a pair of transversely spaced, forwardly extending ears 2I8 on which is pivotally carried a bell crank 2I9. This bell crank forms part of connectible and disconnectible motiontransmitting means, another part of which comprises the circular plate I'I4. The pivot of the bell crank 2I9 on the ears 2I8 is, as shown at 220, in Figure 17, transverse to the axis of the crankshaft I50, so that the lower portion of the bell crank may be swung toward or away from the plate I14. The lower end of the bell crank includes a lug 22I which is selectively engageable 16 with or disengageable from the notch I16 in the plate I14.

The bell crank 2I9 is so formed that it has a rearwardly extending arm 222 which is bent upwardly to provide an attaching ear 223. The position of the bell crank 2I9 is determined by the position of an actuating member 224. This member is preferably triangular in shape and is pivoted at 225 at one apex to a bracket 226 suitably mounted at an upper right hand portion of the bale case 40. Another apex of the triangular member carries a, pin 22! which is received by a slot 228 in the car 223 on the bell crank 2I9. It will thus be seen that rocking of the member 224 about the pivot 225 eifects rocking of the bell crank 2I9 about its pivot 228. Hence, rocking of the triangular member 224 controls engagement or disengagement between the bell crank lug 22I and the notch I16 in the circular plate I14.

The third apex of the triangular member 224 is pivotally connected at 223 to the outer or righthand end of an operating link 230. The opposite or left-hand end of the link 230 is pivotally connected at 23I to the lower end of an arm 232 that is loose on the tier shaft 65 adjacent the forward end thereof, as best shown in Figures 14 and 16. The lower end of the swingable arm 232 is biased toward the left-hand end of the bale case by means including a tension spring 233, one end of which is connected to the arm 232 and the other end of which is anchored at 234 to the top of the bale case 40. Hence, the action of the spring 233 is normally such as to bias the arm 232 for swinging toward the left-hand end of the bale case, thereby acting through the link 230 to pivot the triangular member 224 in a clockwise direction (as viewed in Figure 11) and thereby rocking the bell crank 2I9 in a counterclockwise direction (as viewed in Figure 17) for effecting engagement of the bell crank lug 22I with the notch H6 in the circular plate I74. However. this action of the spring 233 is under the control of means responsive to a predetermined phase in the bale-forming cycle, which will be presently described.

In the conventional baler, the primary interest is in the size of the bales formed in the baling chamber and various types of mechanisms have been heretofore worked out for controlling the operation of the baler in response to the satisfaction of this requirement. One of the most successful devices for this purpose is the so-called measuring wheel; although, other devices have been used. For the present purposes, the responsive device illustrated is in the form of, or includes, a measuring wheel 235. This wheel is carried on a short shaft 236 journaled between the left-hand ends of arms 23'! which are suitably pivotally carried at 238 on an upper portion of the bale case 43.

The measuring wheel has a plurality of peripheral teeth, as shown, which extend through an appropriate slot in the upper wall II of the bale case 40. As the material accumulates in the bale case in response to compression by the plunger 41, the mass of material is gradually worked toward the left-hand or discharge end of the bale case. As the mass moves, the teeth of the measuring wheel 235 engage the material, thus rotating the measuring wheel in increments. Ordinarily, the circumference of the wheel is such that one complete revolution thereof determines a bale having a predetermined desired length. Although the length of the bale bears a direct relationship to its density and therefore will have some effect on the size of measuring wheel used, these considerations may be dispensed with in the present case. Ordinarily, the density of the bale is controlled by relaxing or tensioning portions of the bale case at the discharge end thereof, such as by devices represented by the numeral 239 in Figure 3.

At any rate, the outwardly or leftwardly moving bale causes the measuring wheel 235 to rotate in the direction of the arrow indicated in various figures of the drawings.- The shaft 233 carries thereon a driven arm 240. This arm is separate from the wheel 235 to the extent that both are not keyed to the shaft 236. However, the two are interconnected by driving means including a torsion spring 24 I, so that the ultimate result of rotation of the wheel 235 is to rotate the arm 240 in the same angular phase about the axis of the shaft 236, the torsion spring 24l serving to provide a resilient connection between the wheel 235 and arm 246 as a safety expedient.

The forward end of the shaft 236 has a bearing 242 for rotatably carrying the left-hand end of a transversely extending control rod 243. The opposite or right-hand end of the rod 243 is rotatably carried by a suitable bearing 244 (Figure 16) pivotally mounted on the swingable arm 232 on the front end of the tier shaft 65.

The outer end of the driving arm 246 is provided with a lug 245 which engages a lug 246 rigid on the rod 243. Engagement between the lugs 245 and 246 occurs, of course, during each 360 rotation of the measuring wheel 235 and effects rocking of the rod 243 about its principal axis in the direction of the arrow shown in Figures 15 and 16.

The right-hand end of the rod 243 projects to the right through the bearing 244 on the arm 232 and has keyed thereto a dog or pawl member 247. A torsion spring 248 (Figure 16) is wrapped around the projecting end of the rod 243 and engages against the rear face of the arm 232 and the pawl 24! to normally bias the rod 243 against its direction of angular movement as effected by engagement between the lugs 245 and 246. The pawl 241, in its position as shown in Figure 16, is in the path of intermittent rotation of an arm 249 keyed at 256 to the tier shaft 65. The direction of rotation of the tier shaft is indicated in Figure 16.

The rod 243, in addition to being rockably carried by the bearing 242 on the measuring wheel shaft 236, is also slidable in the bearing 242. The opposite end of the rod or shaft 243 that is carried in the bearing 244 on the swingable arm 232 is provided with a collar 25| that is pinned to the rod 243 by a pin 252. The pawl 247 is likewise pinned or otherwise fixed to the right-hand end of the rod 243 so that the bearing 244 is between the pawl and the collar 25I. Hence, longitudinal shifting of the rod 243 along its principal axis will cause or be effected by swinging of the arm 232, the relationship of which to the operation will be set forth below.

Action of the spring 233 tends to move the swingable arm 232 toward the left hand end of the bale case. However, engagement between the pawl 24? and the arm 249 prevents such shifting of the arm 232. At the same time, the shaft 65 is not rotating and the arm 249 is, of course, stationary. The parts are in the position shown in Figure 11, during reciprocation of the plunger and idleness of the tying mechanism.

Lower wire-carrier and needle guide ccsting- Figures 2.1-25

(Reference numerals 42c, 79, 79a, 253-270) As described above, the bottom wall 42 of the bale case is provided with the opening 42 to accommodate the upwardly moving needles 19. Also, as previously described, the needle guide casting 13 is associated with the opening 42*.

The needle guide castin 19 has an upper web or flange 253 which is rigidly secured to the bottom wall of the bale case. This casting has at each side thereof, and spaced apart on the order of the lateral spacing of the needles 19, depending guide portions 254. Each guide portion has formed therein an elongated slot 255 which runs lengthwise of the bale case and which opens upwardly and downwardly. Each slot is provided intermediate its ends with a pair of vertical recesses 253 which provide guides for guide rollers 251 (Figure 25) on the needles I3. When'the plunger 4'6 is in its compression position, the needle guide tracks 52 therein are respectively in vertical alinement with the roller guides 256 in the needle guide casting 13 The fluid motor I86 for the lower wire guid or carrier I8 is secured to the bottom wall 42 of the bale case, as by a bracket 253. This motor comprises a cylinder 259 and a piston which has a piston rod 260 extending therefrom toward the right side of the bale case. The free end of the piston rod is threaded and passes through an aperture in a transverse plate 26I and receives a nut 262 to secure the plate rigidly thereto.

The plate carries at each side of the piston rod 266' a roller-carrier structure comprising a pair of elongated members 263. Each pair of members is secured at one end to one side of the plate 26I and rides at its other end in tracks 265 formed in the needle guide casting I9 and associated with the respective slots 255 (Figure 22). Each pair of members 263 carries at its free or castingsupported end a pair of wire-carrying rollers 266, each pair receiving the respective lower wire W As best shown in Figures 22 and 24, the bottom wall 42 of the bale case carries a longitudinal slide 261 which cooperates with a slotted portion 268 of the plate 26I to guide the carrier structure back and forth as the motor I83 is actuated. Fluid lines 269 and 216 are shown in Figure 21 as being connected to the motor I86. These lines may be considered to branch off respectively from the lines 20! and 268 for the upper motor I85.

Figure 21 illustrates the retracted position of the carrier members 263; that is, the position in which the rollers 266 are moved out of the path of the upwardly moving needles 19. The corresponding position of the carrier as viewed from above appears in full lines in Figure 22. This figure also shows in broken lines the positions of the rollers when the motor I86 is contracted. In this position of the parts, the arrangement corresponds to that illustrated in Figure '7. Figure 21 corresponds to a phase intermediate that of Figures 8 and 9.

General description of operation When the parts are in the positions shown in Figure 12 of the drawings, the baler is operating with the plunger reciprocating and the tying mechanism idle. This result is achieved because the control valve is in such position that the brake I75 is applied and the holding means I14- I is released. Hence, the circular plate H4 rotates with the crankshaft I60. The tier clutch I32I34 is disengaged. As material is fed through the feed opening ii in the bale case 40 and encountered and compressed by the reciprocating plunger 41, it is moved toward the lefthand or discharge end of the baler, thus rotating the measuring wheel eventually through one complete revolution, in response to which the control rod 243 is rocked to effect engagement of the bell crank lug 22I with the notch I16 in the rotating plate I14.

As the rotating plate I14 engages the bell crank lug 22l, the control arm 2I2 is caused to swing toward the right-hand end of the bale case against the tension of the spring 2|6, thu moving the control valve member 208 to the position shown in Figure 13. This action of the control valve reverses the action of the control means on the epicyclic gear train, thus releasing the brake I15, and simultaneously effecting engagement of the tier clutch I32I34 and retraction of the wire uide carriers 14 and 18. The motion-transmitting connection effected by the notch I16 and bell crank lug 22I serves also as means for stopping the crankshaft I14. However, in order that the crankshaft will be stopped only when the plunger is on its compression stroke, the indexing means comprising the notch I11 and lug I80 on the lever I81 takes effect, the angular position of the notch I11 on the plate I14 being properly timed with the crank throw I54.

Completion of the tying operation is effected in one revolution of the tier shaft 65, following which the previously released arm 249 on the tier shaft recngages the pawl 241 on the trip rod 243 to ultimately release the bell crank lug 22I from the notch I16 in the plate I14. Thereupon, the spring 2 I6 retracts the arm or control plate 2I2 toward the left-hand end of the bale case and again shifts the shiftable valve member 200 to the position of Figure 12, again incurring idleness of the tying mechanism and mobilizing or operation of the plunger 41.

Thus it will be seen that the automatic operation of the baler is dependent upon the satisfaction of three basic requirements, namely, the accumulation of a predetermined quantity of material in the bale case and attainment by the plunger of a position at or substantially at the end of its compression stroke, and completion of the tying operation. The first two are characteristic of two different phases in the bale-forming operation; and the third requirement is a characteristic of the bale-tying operation.

Specific description of the operation The condition in which the parts occupy the positions shown in the main figures of the drawings, and particularly the relationship of the control means as illustrated in Figure 12, is a normal condition incident to starting up the baler, in which case it will be assumed that the bale case is empty. The control member or plate 2I2 is dependent upon actuation in the first instance by the tension spring 2 I6, which normally maintains the plate 2 I2 so that the upper end thereof is swung toward the left-hand end of the bale case 40. This means that the control valve member 20!! is in the position shown in Figure 12.

When the baler is started, power supplied from the initial source (here through the propeller shaft I08) is transmitted through the sheaves and belts to the sheave I26 of the epicyclic driving mechanism. At the same time, the pump sheave I9I is driven to incur operation of the pump I90 to supply fluid under pressure to the motors IBI and I84 and to the right-hand end of the twoway wire guide motor I82. The motor IBI retracts the index lever I18 so that the plate I14 on the plunger crankshaft I50 is disengaged and allowed to rotate as the plunger reciprocates. Simultaneously, the motor I84 effects energizing of the brake I15 to hold the tier output drum I58 and member I28 demobilized or stationary. Also simultaneously, the motor I42 is exhausted through the left-hand end of the motor I85 so that the tier clutch is disengaged.

Material fed by the feeding means 36 passes through the inlet opening 46 in the front wall of the bale case 40 and is compressed by the plunger into a bale. As the bale moves toward the discharge end of the bale case and increases in length, the measuring wheel 235 is rotated in a counterclockwise direction as viewed in Figure 11. As the measuring wheel completes one revolution, the arm 240, by virtue of the lug 245 thereon, engages the lug 246 on the trip rod 243, thereupon rotating the pawl or dog 241 in such manner that it escapes from the latching or looking efiect of the arm 249 that is keyed to the tier shaft 65 (not stationary) When the pawl 241 is thus released from the stationary arm 249, the spring 233 rocks the arm 232 about the axis of the shaft 65 in the direction of the arrow A in Figure 16 (or toward the lefthand end of the bale case), the initial tension in the spring 233 being responsible for this effect. This action of the spring 233 and arm 232 causes the link 230 to be shifted toward the left-hand end of the bale case, thereby rocking the triangular member 224 in a clockwise direction (as viewed in Figure 11) about its pivot 225. The member 224 thus depresses the inner end of the bell crank H9 and rocks the bell crank about its pivot 220 so that the lug 22I thereon moves forwardly and into the path of the notch I16 in the rotating plate I14.

As previously described, the rotating plate thus picks up the bell crank 2I9 and, since the bell crank is connected to the control member 2I2, shifts the control member toward the right-hand end of the bale case and against the tension of the spring 2I6. This movement of the control member effects, as aforesaid, shifting of the control valve member 200 to the position shown in Figure 13.

As soon as the driving member 248 on the measuring wheel shaft 236 has engaged and rocked the trip rod 243, the lugs 245 and 246 separate. The trip rod 243 then rotates in the reverse direction under action of the torsion spring 248, thus restoring the pawl or dog 241 to the position shown in Figure 16. In the meantime, shifting of the control valve member 260 to the position of Figure 13 has reversed the mobilizing and demobilizing of the output members in the epicyclic gear train so that the tying mechanism has been started and the arm 249 on the tier shaft 65 has now moved past the restored pawl 241.

Description of the tying operation Initiation of the tying operation is, as af0resaid, effected by demobilizing of the plunger crankshaft because of engagement between the plate I14 and control member 2 I2. As the memher 224 rocks through the angular range sufficient to shift the control member, the notch I11 in the plate becomes alined with the lug I on the index lever I18. Before that, the control member eliminating undesirable slack in the wires.

has shifted the valve so that the motor IBI is exhausted, whereupon the spring I83 behind the index lever I18 is conditioned to move the index lever in such manner as to effect engagement between the lug I80 and the notch Ill. The plunger is thereupon held at the end of its compression stroke. The index means further provides locking means for preventing retrograde movement of the plunger and thus eliminates any possibility that the control member 2I2 could inadvertently shift back toward the left-hand end of the bale case and disrupt the tying operation.

Upon reversal of the application of fluid pressure, fluid is exhausted from the left-hand end (as viewed in Fig. 12) of the wire guide carrier motors I85 and I86 and is applied to the righthand ends of the motors and simultaneously through the conduit 299 to the tier clutch motor I42. Substantially simultaneously with mobilizing of the tier output sheave I28, the tier clutch I32I34 is engaged, whereupon the tying mechanism is actuated as described above.

When the upper portion of the tying mechanism, namely, the tying mechanism housing 55, is in its upper position, it is remote from the bale case and is free from the upper wires W. In this position, the housing 54 is out of the path of flying dust and fragments of hay or straw that are incident to the usual baling operation. Further, freedom of the twister and kinker gears from the upper wires W means that these wires can lie more closely proximate to the bale, hence The same results in general occur at the lower portion of the bale case. That is, the lower wires W are held by the rollers 296 in close proximity to the bottom of the bale and these wires are free from or not engaged by the rollers 94 of the needles 19.

The simultaneous retraction of the carriers 15 and 1B and the simultaneous movement of the tying components 54 and 19 to cooperative tying positions have been described above and need not be repeated.

The relationship of the lower wires W to the needles 19 should be noted in one particular respect. That is, the wires W extend along the bottom of the bale and thence upwardly to the point where they are united with the upper wires W at knot K. As the needles 19 move upwardly to bring the wires W into proximity to the downwardly moving tying mechanism housing 54,

the wires W are tightened about the bale and the necessary length thereof is payed out from the lower wire coils C It sometimes happens in balers and other machinery equipped with tying mechanism, that the tying operation fails for some reason or another. If such failure should occur in the present case, it would not be necessary to re-thread the needles 19, since the wires W are engaged only by the upwardly moving needle and are not in any way wrapped around the rollers 94; In prior constructions, in which the wires or twine is threaded through the needles, the machine must be stopped while the needles are re-threaded every time a miss occurs in the tying mechanism.

As the tier shaft completes one revolution to effect the tying operation, the arm 249 keyed at 250 to the forward end of the shaft 65 again approaches the pawl 241. The spring 233 is now holding the arm 232 in a position more toward the-left-hand end of the bale case'than'the position shown in Figure 11. The pawl 24'1Iis fixed tothetrip rod '2 43"at'oneside of thebearingm,

and since the collar 25I is pinned at 252 to the rod 243 at the other side of the bearing 244. the pawl 241 likewise is in a position toward the left-hand end of the bale case. Now, the angularly moving arm 249, approaching the end of its travel through 360, engages the pawl 241 and shifts the pawl and consequently the arm 232 toward the right-hand end of the bale case against the tension of the spring 233. This action effects shifting of the link 230 toward the right-hand end of the bale case and the link effects rocking of the triangular member 224 in a counterclockwise direction (as viewed in Figure 11) about its mounting pivot 255. This rocking of the member 224 elevates the inner upper end of the bell crank 2 I9 and swings the bell crank lug 22I out of engagement with the notch I16 in the now stationary plate I14. Since the control member 2I2 is loaded byithe spring 2I6,'the .obvious result is thatthe control member swings toward the left-hand end of the bale case. This action of the control member re-shifts the control valve member 200 from the position ofFigure 13 to the position of Figure 12 and againreverses the effect of the fluid-pressure system. That is, the motors I8I and I84 are againxsubjected to pressure, with the result that the index lever I18 is moved again to the position of Figure '11 and the brake I15 is again energized to demobilize the tier output member or element I28I58. Simultaneously, the tier clutch motor I42 is exhausted through the conduit 209, the left-hand end of the motor I85 and conduit 201, along with re-shifting of the wire guide carriers 14 and 18 to the positions they occupy while the bale is being formed.

The operative cycles described above will continue as long as the baler is receiving material to be baled and tied. Obviously, if the pick-up takes in no more material to be fed to the baling chamber, the tying mechanism will cease to operate after the last bale has been tied and the plunger will continue to reciprocate until the application of power to the propeller shaft I08 is discontinued.

Swmmary The preferred embodiment of the invention illustrated in the drawings and described above is admirably adapted to accomplish the several objects hereinbefore set forth and other objects mentioned as an incident to the description of the structure and operation of the baler. Other objects not specifically enumerated or otherwise set forth will undoubtedly occur to those versed in the art, as likewise will various modifications and alterations in the preferred structure illustrated, all of which may be achieved without departing from the spirit and scope of the invention as defined in the appended claims.

What is claimed is:

1. In a baler; means forming an elongated bale chamber having first and second walls spaced apart across the chamber, each of the walls having an opening therein and said openings being alined crosswise of thechamber; baleforming means including a member movable lengthwise of the chamber to compress material therein, said member having a track therein crosswise thereof so as to .become at times alined with the aforesaid openings; drive means for. the bale-forming means demobilizable to halt the bale-forming means with the track and openings in alinement; means supported outside the first wall including .a guideway alined with .the first wall opening; strand-passing means movable 

